Transmission and controller



Nov. 24,1942.

W. 1.. j POLLARD TRANSMI S S ION AND CONTROLLER Filed April 7. 1941 s Sheets-Sheet 1 Nov. 24, 1942.- w. 1.. POLLARD TRANSMISSION AND CONTROLLER 6 Sheets-Sheet 2 Filed April 7, 1941 %//W%% a, V

mlllllllllllllllll lllll Nov. 24, 1942. w. L. POLLARD ,3

TRANSMISSION AND CONTROLLER Filed April 7, I194]. 6 sheets Sheet 5 Nov. 24, 1942. w.. L. POLLARD 2,302,714.

TRANSMISSION AND CONTROLLER I Filed April 7, 1941 s Sheets-Sheet 4 Nov. 24, 1942 i w. POLLARD 2,302,714

' TRANSMISSION AND CQNTROLLER Filed April 7, 1941 6 Sheets-Sheet 5 Nov. 24, 1942. w. L, POLLARD TRANSMISSION AND CONTROLLER Filed April 7, 1941 e Sheets-Sheet 6 Patented Nov. 24, 1942 UNITED s'ra'riszs PATENT OFFICE TRANSMISSION AND con'rnonmm Willard L. Pollard, Evanston, 11]. Application April 7, 1941, Serial No. 387,174

8 Claims.

My invention relates to variable lag fluid transmissions and controlling means therefor.

One of the objects of my invention is to pro-.- vide improved means controlled by the variable lag or lead in a fluidtransmission for controlling the selection from a plurality of stages of different relative speed ratios. 7

A further object of my invention is to provide such a transmission and control in which means are provided for preventing the variable lag from exercising control over a certain speed range.

Further objects and advantages of the invention will appear from the description and claims.

of Fig. 5, combined diagrammatically with anaxial sectional view of a hydro planetary transmission, parts being broken away;

Fig. 7 is a detail sectional view on the line 'l1.of Fig. 6;

Fig. 8 is a sectional view showing another form of transmission and controller;

Fig. 9 is a side elevational view showing another form of controller, parts being broken away;

Fig. 10 is a sectional view of part of the controller, with the parts in a different position from that shown in Fig. 9;

Fig. 11 is a view similar to Fig. 10, with the parts in still another position;

Fig. 12 is a sectional view showingthe parts of Fig. 11 in still another position;

Fig. 13 is an axial sectional view of a transmission controllable by the controller shown in Fig. 9. s

Fig. 14 is an axial sectional-view showing another form; and

Fig. 15 is an axial sectional view showing another form.

Referring to the drawings in detail, and first to Figs. 1-4, inclusive, the construction shown comprises a drive shaft I, a driven shaft 2, an intermediate shaft 3, a fluid torque converter 4,

a clutch lfor connecting and disconnecting the intermediate shaft 3 with respect to the drive shaft I, a planetary transmission 6 comprising a ring gear I splinedto the intermediate shaft 3,

a gear carrier 8 splined to the driven shaft 2, a sun gear 9, a planet gearing l0 carried by the gear carrier 8 and meshing with the sun gear 9 and ring gear 8-, a one-way coupler or gripper II for preventing reverse rotation of the sun gear, a one-way clutch l2 for preventing the sun gear 9 from overrunning the turbine rotor, a clutch I3 for connecting and disconnecting the statorotor ll with respect to the turbine rotor l5, a one-way coupler or anchorage l6 for preventing reverse rotation of the stato-rotor M, a one-way clutch I! for preventing the stato-rotor from overrunning the turbine rotor I 5, and a pump rotor l8 secured to the drive shaft l.

transmission, I will briefly describe the opera- .tion of the transmission. For high torque ratio,

the clutch I9 is conditioned to connect the intermediate shaft 3 and ring gear 1 to rotate with the turbine rotor I 5, the other clutches 5, I3, and 20 all being disconnected. In this condition, the one-way anchor ll holds the sun gear 9 against reverse rotation, and the ring gear I is driven from the turbine rotor 15, driving the planet gearing l0, gear carrier 8 and driven shaft 2, the shaft 2 being driven at a lower rate of speed than the ring gear 1. For a higher speed of the driven shaft, the clutch 20 is conditioned to connect the sun gear 9 to rotate with the turbine IS, the clutch l9 remaining connected. Under these conditions, both the sun gear 9 and ring gear I are connected to rotate with the turbine rotor l5 so that the .driven shaft 2 rotates in unison with the turbine rotor I5. When the drag on the driven shaft 2 becomes small enough with respect to the torque available at the drive shaft 1, a more eflicient stage may be used by connecting the clutchi and disconnecting the clutch l9. Under these conditions, the power flow is divided, the ring gear I being connected direct to the driveshaft I and the sun gear 9 being connected to rotate with the turbine rotor I5.

In order to transform the action of the fluid part of the transmission from torque conversion to pure coupling, the clutch I3 is conditioned to connect the stato-rotor l4 direct with the turbine rotor I 5.

The apparatus for controlling these various clutches comprises two speedometers and various circuit controllers and circuits controlled by these two speedometers. One of the speedometers is driven from the flexible shaft 2| which in turn is driven from the drive shaft I, which speedometer controls the angular position of the shaft 25, mesh with gears 30, 3|, 32, and 33,-re-

spectively, which are rotatably mounted on the speedometer shaft 22. The hubs of these gears 30, 3|, 32, and 33 have mounted thereon contact fingers 34, 35, 36, and 31, respectively, which are engageable and disengageabl'e with respect to th contact plate 38 carried by the disc 23.

A lost-motion connection may be provided, if desired, between the hub of the gear 33 and the contact finger 31, as shown in Fig. 1, and a similar lost-motion arrangement may be provided between the hubs of the gears 32, 3|, and 30, and the fingers 36, 35, and 34 carried by these hubs in order to prevent hunting action of these fingers when the fingers are close to the edge of the contact plate 38. The gears are so designed that the gear 33 will be rotated at the same angular speed as the shaft 25 which carries the gears 28, 28, 21, and 26. The gear 32 will be rotated at a higher angular velocity than the shaft 25. The gear 3| will be rotated at a higher speed than the gear 32 and the gear 30 will be rotated at a still higher speed than the gear 3|. It will be noted that all of the gears 33, 32,.3l, and 38 have their angular position controlled by the speed of the driven shaft so that the angular positions of the contact fingers 31, 36, 35, and 34 also will have their angular position determined by the speed of the driven shaft. The angular position of the contact-carrying disc 23 is dependent on the speed of the drive shaft I, which speed is'the same as the speed of the pump rotor 4. The contact fingers and the contact 38 on the disc are so designed and positioned that when the drive shaft and driven shaft 2 are stationary, none of the contact fingers will bein contact with the contact plate. When the drive shaft is caused to rotate, the drag on the driven shaft will cause a lag of the driven shaft with respect to the drive shaft, so that the contact plate 38 I8. is connected through the conductor 63, switch 44, and conductor to a contact 46 which is always in engagement with a contact ring on the hub of the intermediate contact finger 35. The electromagnet 41 which, when energized, con nects the intermediate shaft 3 with the drive shaft I, is connected through the conductor 48, switch 44, and conductor 45 to the same contact finger 35. The electromagnet 49 which, when energized, connects the stato-rotor i4 with the turbine rotor I5, is connected through a conductor 58, switch 5|, and conductor 52 to a contact :5: engaging the hub of the intermediate finger The hub of the other contact finger 31 is en-- small contact plate60 mounted on the disc 23 will move still farther away from the contact fingers. However, when the conditions are such that the lag of the driven shaft with respect to the drive shaft decreases, the contact fingers will begin to catch up with the contact plate on the disc, due to the speed multiplication effect of the gears. As the lag decreases still further, the contact finger 34 will catch up with the contact plate. In a similar manner, when the lag of the turbine rotor with respect to the pump rotor decreases further, the succeeding contact fingers 35, 36, and 31 will successively catch up with the contact 38 on the disc 28, the gears and speedometers being so designed that this will be accomplished.

I will now describe the circuits by which the contacts and contact fingers control the circuit for the clutches. The electromagnet 38 for the clutch which controls the action of the sun gear 9 with respect to the turbine rotor I5 is connected by a circuit 48 to a contact 4| which is always in engagement with the hub which carries the short contact finger 34. The electromagnet 42 which, when energized, disconnects the clutch and electrically connected with the contact plate 38 by means of rivets 5|. The fixed contact 53 and the small movable contact" are so placed relative to each other that they will not be in engagement with each other until the motor shaft i has attained a speed at which the motor will be operating with a reasonable degree of efficiency.

In operation, with the car standing still and the motor shaft idling but increasing in speed, when the speed of the motor becomes such as to bring the contact 58 in engagement with the fixed contact 58, the contact plate 38 will be energized.

As the driven shaft 2 starts to move and increases in speed, the contact fingers 34, 35, and 38 will be successively brought into engagement with the contact plate 38, and will remain in engagement with this plate until the speed of the driven shaft 2 with respect to drive shaft i begins to decrease. It may be assumed that the speedometer gears are so designed that the contact finger 34 will engage the contact plate 38 at a speed ratio of driven shaft 2 with respect to drive shaft of .36; that the contact finger 35 will be brought into engagement with the contact plate 38 when the above speed ratio reaches .55; that the contact finger 38 will be brought into engagement with the contact plate 38 when the above speed ratio reaches .85; and that the contact finger 31 will not be brought in engagement with the contact plate 38 until the speed of the driven shaft 2 exceeds the speed of the drive shaft this latter situation arising when the driven shaft 2 becomes the drive shaft, and the drive shaft v| becomes the driven shaft, as may happen when going downhill, the accelerator pedal is released, or when coasting to a stop on level roadway.

At the instant the contact finger 34 catches up with the contact plate 38, the overall speed ratio is .36 and the speed ratio of the turbine rotor |5 with respect to the pump rotor I8 is approximately .55. Immediately after the contact finger 34 engages the contact plate 38, the speed ratio of the turbine rotor with respect to the pump rotor will drop materially until the torque ratio increase will be sufiicient to equalize the drag.

up with the contact plate 38, the overall speed is.

.55 and the speed ratio of the turbine rotor with respect to the pump rotor is also .55.

At the'instant the contact finger 38 catches QTI.

, and 38 are noteflective to control transmission vaction below this point C on the motor curve,

up with the plate 38, the overall speed ratio is .85 but the speed ratio of turbine to pump is still only about .55.

So long as the overall speed ratio remains below .36, the clutch I9 will be connected, and the clutches 5, I3, and 28 will be disconnected. When the speed ratio reaches .36, the contact finger 34 will engage the contact plate and energize the electromagnet 39 to connect the sun gear 9 to rotate with the turbine rotor I5, the sun gear 9 and ring gear I being thus both rotatable with 1 the turbine I5. This change in the drive may cause somefiuctuation of the speedometer shaft with respect to the speedometer shaft 32, but due to the lost motion connection between the contact finger 34 and the speedometer transmission, the contact 34 will remain in engagement with the contact plate 38, and thus avoid a hunting action of the contact finger.

If the driven shaft 2 continues to pick up in speed with respect to the drive shaft I, the contact finger 35 will engage the contact plate 38 when the speed ratio becomes .55. At this point the contact finger 35 will engage the contact plate 38 and the electromagnet 41 will be energized to connect the intermediate shaft 3 with the drive shaft I, and the electromagnet 42 will be energized to release the clutch I9 from connection with the turbine rotor I5. A spring means 69a, acting on the clutch I9 is provided for holding the clutch I9 normally in connecting position with the electromagnets.

With the electromagnets 41 and 42 energized, the intermediate shaft 3 is connected to rotate with the drive shaft I, and is disconnected from the turbine rotor l5. Under these conditions the sun gear 9 is connected to rotate withthe turbine rotor I5 so that a divided power flow isobtained between the drive shaftl and the driven shaft 2, resulting in an increase in efficiency, since only part of the power is transmitted through the hydraulic part of the transmission.

If the driven shaft continues to pick up in speed, with respect to drive shaft I, the contact finger 36 will engage the contact plate 38. This will energize the electromagnet 49, causing the clutch I3 to connect the stato-rotor I4 with the turbine rotor I5.

This transforms the hydraulic part of the transmission from a torque converting action to a slip coupling action. This transformation may be made to take place at any desired part of the efficiency curve A of a fluid torque converter shown in Fig. 4. v

It will be seen that the points of changeat the overall speed ratios of .36', .55, and .85 cause the hydraulic. part of the transmission to operate on a relatively high portion of the efliciency curve not extending beyond the ratio of .55 between turbine and pump, thus confining the action of the torque converter in the higher speed ranges to a relatively high efficiency part of the curve. The fixed contact 58 and the movable contact 88 may be so designed asto cause the energization of the contact plate 38 at any desired point on the efilciency curve B ofthe motor shown in Fig. 3. For example, the apparatus may be so designed that contact will be made at the point C which is about 40% of full motor speed. 1 At this point the motor is operating at relatively high efficiency.

It will be noted that the contact fingers 34, 35,

as the contact 38 is not energized until this point on the motor curve is attained.

If the speed of the driven shaft 2 becomes greater than the speed of the driving shaft I, as for example in coasting downhill or in coming to a stop on level roadway, the contact finger 31 will engage the contact plate 38. This will energize the electromagnet 48 opening the switches 44 and 5|. This will deenergize the electromagnets 41, 49, and 42. This will disconnect the intermediate shaft 3 from the drive shaft I, disconnect the stato-rotor I4 from the turbine rotor I5, and will allow the spring to cause the clutch I9 to connect the intermediate shaft 3 and ring gear I with the turbine rotor l5. This will cause the engine to exert a'braking eflect in coasting downhill or in coming to a standstill on level roadway.

To effect a reverse, the planet carrier 8 and ring gear 9 are shifted rearwardly.- This disconnects the gear carrier from the driven shaft 2 and connects it with the nonrotatable dog clutch ring 82 to hold the gear carrier against rotation. It also disconnects the ring gear I from the intermediate shaft 3 and connects it with the dog clutch ring 63 on the driven shaft 2. The planet gears III remain in mesh with the sun gear 9. Under these conditions, when the sun gear 9 is driven in one direction. the ring gear I will be driven in the reverse direction and will carry with it the driven shaft 2.

The construction shown in Figs. 5.7, incl.,'

meshing with the planet gearing and keyed to the driven shaft, a sun gear 81 meshing with the planet gearing, a pump rotor 88, a clutch housing 89 secured to rotate with the pump rotor, a twoway clutch III which, in one condition, connects the clutch housing to rotate with the gear carrier 84, and, in another condition; connects the clutch housing to rotate with the sun gear 81, a one-way clutch 'II which prevents the drive shaft I from overrunning the clutch housing 69, a turbine rotor I2 keyed to the driven shaft 2, a one-way'reaction stato-rotor I3 acting between the pump rotor and turbine rotor,'a one-way anchoragedevice 14 for preventing reverse rotation of the state-rotor, and a clutch I5 for connecting and disconnecting the pump rotor .88. A speedometer drive I8 is provided, driven from the drive shaftl, and another speedometer-drive II, driven from the driven shaft. A suitable fluid actuated controller I8 is provided for controlling the two-way clutch I8 and another fluid actuated controller I9 for controlling the rear clutch I5.

When the two-way clutch I3 is positioned to connect the pump rotor 68 with the gear carrier 65, the drive is from the motor shaft I, through the gear carrier 84, pump rotor 68, stato-rotor I3, and turbine rotor I2 to the controller shaft.

When the two-way clutch I3 is positioned to connect the pump rotor 88 with the sun gear 61,

the power flow is divided. One path is from the motor shaft I, through the gear carrier 94, planet gearing95 and ring gear 99 to the driven shaft 2. through the gear carrier, planet gearing, sun gear, pump rotor, state-rotor, and turbine rotor to the driven shaft. In this position the torque multiplication is less than in the first position,- but an increase in efllciency results, since only a fraction of the power goes through the hydraulic part of the transmission.

When the clutch 19 is operated to connect the.

state-rotor with the pump rotor, the hydraulic part of the transmission ceases to act as a hydraulic torque converter and begins to operate as a hydraulic coupler.

The controller device for the transmission comprises a shaft 89 driven from the front speedometer shaft 19, another shaft 9i driven from the rear speedometer shaft 11, a valve 922 for controlling the front fluidpressure actuator 18, and a valve 83 for controlling the rear fluid pressure actuator 19. The valve 82 is connected with the actuator 19 by means of a suitable tube or pipe 99, and the other valve 99 is connectedwith the other actuator 19 by means of another tube 95. Fluid under pressure is supplied to these valves by means of the tubes 99. The two valves 92 and 99 are controlled by means of a pair of arms 96 and 91, respectively, mounted on a rock shaft 88, the movement of which is controlled by the relative speed of the drive shaft I and driven shaft 2. The means for controlling this rock shaft 98 comprises 'a friction wheel 89 splined on a shaft 99 driven from the rear speedometer shaft 11 having a grooved shifting collar 9| which engages the swinging end of the rock arm 92 on the rock shaft 99, which wheel 99 adjusts itself automatically along the face of the friction disc 99 and assumes a position which is a function of the relative speed of the two speedometer shafts 19 and 11. To enable the self-adjusting action, the shaft 99 on which the friction wheel 89 is splined has a universal joint connection 99 with the shaft 95, which is driven from the rear speedometer shaft 1'1, and the end of the shaft remote from this universal joint is floatably mounted in a floating bearing 99 (Fig. '7), which enables the shaft to have a limited swinging movement under the face of the disc 99 which is driven from the front speedometer shaft 19. To secure the desired speed of the shaft 99, a suitable gear box 91 may be provided. A oneway clutch 98 is provided between the shaft 99 and the output shaft 99 for a purpose which will appear hereinafter. A coil compression spring I99 (Fig. '7) is provided for pressing the floating bearing 99 toward the face of the friction disc 99. It may be assumed that the parts are arranged so that the disc 99 rotates in a clockwise direction, as seen in Fig. 6, and that when the friction wheel 99 rotates in a counterclockwise direction, as seen from the right in Fig.5, the one-way clutch 99 will permit only counterclockwise motion to the shaft 99, and that the gear box 91 is of such ratio that when the speed ratio of the drive shaft I and driven shaft 2 is 1:1, the peripheral speed of the friction wheel 89 will be equal to the surface speed of the friction disc 99 near its periphery.

- In operation, the wheel 99 will shift to and fro on the splined shaft 99 in such a way that it will contact the friction disc 99 at a point where the surface speed of the friction disc 99 is equal to the peripheral speed of the friction wheel 99.

The other path is from the drive shaft I,-

The reason for this is that if the Peripheral-speed of the wheel 99 is greater than the surface speed of the disc 99, the shaft 99 will be tilted in a clockwise direction, as seen in Fig. 6, about the universal Joint 94 so that the wheel 89 will tend to crawl outwardly with respect to the friction disc, and vice versa, if the peripheral speed of the friction wheel 99 is less than the surface speed of the friction disc 99, the spring I99 will exert its horizontal component of force to tilt the shaft 99 counterclockwise and cause the friction wheel 99 to crawl inwardly.

The one-way clutch 99 is provided in order to allow the driven shaft 2 to remain stationary while the motor shaft I stillrotates, in which case the friction wheel 99 will shift to the left to a point near the center of the friction disc 99 and in that position will be driven to overrun the shaft 99 without grinding against the disc 99.

In operation, if the shaft 2 is initially standhas still, the friction wheel 99 will beclose to the axis of the friction disc 99. As the shaft 2 picks up in speed with respect to the motor shaft I, the friction wheel 99 will crawl to the right, as seen in Fig. 6. This will move the rock arm 92 in a counterclockwise direction. This will first cause the arm 99 and valve lever IN to operate the valve 92 to supply fluid to the actuator 19 to disconnect the pump rotor 98 from the gear carrier 94 and connect it with the sun gear 91. As previously explained, this will result in a decrease in the maximum torque available but will also result in an increase in efllciency.

If the speed of the driven shaft 2 with respect to the drive shaft I continues to increase, the

-friction wheel 99 will move still-further to the right, as seen in Fig. 6, and will cause the arm to engage the valve lever I92 and supply fluid to the actuator 19 to cause the clutch 15 to connect the stato-rotor 13 to rotate with the pump rotor 99. When this takes place, the hydraulic part of the transmission will cease to act as a hydraulic torque converter and will begin to act as a hydraulic coupler. It will be seen that by choosing the relative dimensions of the controller, the changes from high torque to low torque drive and from hydraulic converter action to hydraulic coupler action maybe made to take place at any desired relative speed of the driven shaft with respect to the drive shaft, and hence at any desired point on the eihciency curve of the hydraulic part of the transmission.

The construction'in Fig, 8 comprises a turboplanetary transmission and control apparatus therefor. The turbo-planetary transmission comprises a drive shaft I9I, adriven shaft I92, a gear carrier I99 keyed to the drive shaft, planet gearing I 99 carried by the gear carrier, a sun gear I meshing with the planet gearing, a oneway anchor I99 for preventing reverse rotation of the sun gear, a ring gear I91 meshing with the planet gearing and keyed to the driven shaft I92, a pump rotor I99,a one-way clutch I99 for preventing the gear carrier from over-running the pump rotor, a reactance stator II9, a oneway anchor III for preventing reverse rotation of the stator, a turbine rotor II2 keyed to the driven shaft, clutch mechanism comprising a clutch casing III keyed to the sun gear, a clutch plate ill for connecting and disconnecting the gear carrier with respect to the clutch casing, and a clutch plate II 9 for connecting and disconnecting the pump rotor with respect to the clutch casing, a speedometer gear II9 driven from the drive shaft, a speedometer gear II1 driven from the driven shaft, a hydraulic actuator 8 for controlling the action of the clutch plate II4,

a hydraulic actuator I I9 for controlling the action of the clutch plate 5, a brake I20 for bolding the clutch casing against rotation, and a hydraulic actuator I2I for controlling this brake.

The control mechanism includes a rotatable screw-threaded shaft I22 driven from the speedometer shaft I23, a shaft I24 driven from the other speedometer shaft I25, a pair of internally threaded spur gear I26 and I21 threaded on the threaded shaft, collars I28a, I28b, and I280 fast on the shaft I22 for limiting the spiral movement of the spur gears I26 and I21 on the screw-threaded shaft, frictionally driven spur pinions I29 and I30 mounted on the shaft I24, friction washers I3I splined on this shaft I24 engaging the sides of the gears I29 and I30, collars I32 fast on the shaft I24 to prevent endwise slip of the pinions I29 and I30, a coil compression spring I33 urging the friction washers I3I against the sides of the gears and valve mechanism controlled by the axial component ofthe spiral movement of the gears for controllin the action of the fluid pressure actuator.

This valve mechanism is controlled by the shifter arms I34 and I35 engageable with annular grooves in the gears I26 and I21, respectively. The valve mechanism controlled by the right-hand gear I21 comprises a valve I36 to which the shifter arm I35 is secured, controlling the flow from the tube I31 to the tube I38 leading to the actuator H9. The valve mechanism controlled by the left-hand gear I26 comprises valve I40 controlling the flow from the tube :I4I

, to the tube I42leading to the actuator H8, and

a valve I43 controlling the flow from the tube I44 to the tube I 31. It will be noted that the valve I 43 is in series flow relation with respect to the valve I36.

The control valve mechanism further includes a duplex valve I45, one portion of which controls the flow from the pressure supply tube I46 to the tube I41 leading to the actuator I2I and the other portion of which controls the flow from the tube I48 to the tube I4I. This valve I45 may be manually controlledor may be controlled by abnormal movements of the accelerator pedal. The valve mechanism also includes a valve I49 for controlling the flow from the pressure supply tube I50 to the tube I48, which valve I49 is in series flow relation with the right-hand portion of the manually-controlled valve I45 and also in ser es flow relation with respect to the gear-controlled valve I40. This valve I49 may be controlled in any suitable manner as by motor speed which may be the speed of the shaft IN. The c ntrol valve mechanism also includes a valve II controlling the flow between the pressure supply tube I44 and the tube I31 which also may be c ntrolled by the speed of the shaft IM and which valve is in series flow relation with respect to the valve I43 and the valve I36.

The transmission may operate under four different conditions as follows: (1) high torque condition, in which both clutch plates H4 and H5 are free and the brake I20 is free; (2) efficient torque converter action, in which the clutch plate H5 is connected. the clutch plate H4 and the brake I20 being still disconnected; (3) direct drive, in which the clutch plate II 4. is

connected, the brake I20 being still disconnected and it being immaterial whether or not the clutch plate H5 is connected; (4) overdrive, in

I08, stator I I0 and turbine rotor I I2-to the driven shaft I 02. In the second of the above conditions, there is a divided flow of power between the shafts IM and I 02, one path being from the gear carrier I03, through the planet gearing I04 and ring gear I01 to the driven shaft I02,-and the other path being from the gear carrier I03, through the sun gear I05, clutch housing H3, clutch plate II5, pump rotor I08, stator I I6 and turbine rotor II2 to the driven shaft I02. In the third condition, there is direct drive, since the sunrgear I 05 is directly connected with the gear carrier I03 through the clutch housing H3 and clutch plate II4. In the fourth condition, there is a gear overdrive as the sun gear is held against rotation by the brake I20 and the ring gear will be driven at a higherrate of speed than the gear carrier I03.

The gears I21 and I 29 have their pitch diameters so proportioned that at a certaindefinite speed ratio of driven shaft I02 with respect to drive shaft IOI, the roles of driving member and driven member with respect to the gears I21 and I29 will be reversed. For example, the pitch diameters of the two gears I21 and I29 may be so designed that below a speed ratio of .6 of driven shaft I02 with respect to drive shaft IOI, the gear I29 will be exerting a driving force or pull on the gear I21 which will hold this gear I 21 against stop collar I20a, thegear I29 slipping on the shaft I24 by reason of the slip friction drive exerted by the friction discs I3I and I32. When, however, the speed of the driven shaft I02 with respect to the drive shaft l0! rises above the ratio .6, the gear I 21 will try to run ahead of the gear I29, but as the gear I29 will then exert a drag on thegear I21, the gear I21 will travel in a spiral path along the threads of the shaft I 22 until the gear comes into engagement with the stop shoulder I28b. Thereafter the gear I29 will again slip on the shaft I 24, due to the slip drive of the friction discs I3I and I 32. When the gear I21 moves as above described from engagement with the stop collar I28a into engagement with the stop collar I28b, it will act on the shifter arm I35 to move the valve I36 from closed to open position. This shift will take place at a speed ratio of turbine to pump of 6 where the efficiency of the converter may have fallen to about In a similar manner, the pitch diameters of the gears I28 and I30 may be so designed that with a definite speed ratio of driven shaft I02 with respect to drive shaft IOI, the gear I26 will be shifted from' its left-hand position where it engages the stop collar-I280 to the right-hand position in which it engages the stop collar mm. This lateral shift of the gear I26 will act on the shifter arm I34 to move the valve I40 from closed to open position and also to move the valve I43 from open to closed position. The point chosen in the speed ratio scale of driven shaft I 02 to driving shaft IOI for this shifting of the gear I26 may be about .82, at which time the speed ratio of turbine to pump will again be about .6.

As previously indicated, the valves I49 and I5I may be controlled by the speed of the motor.

For example, the valve I5I may be controlled so that it will remain closed until the speed of the motor reaches, .for example, 900 R. P. M., after which it will remain open. The valve I40 may be so controlled that it will remain closed until the speed of the motor reaches, for example,

1200 R. P. M., after which it will remain open.

The valve I45 may bemanually controlled and may be made to occupy any one of three different positions. In its intermediate position, it provides communication between the tubes I46 and HI In its left-hand position, it closes communication between the tubes I40 and I and opens communication between the tubes I40 and I41. In its right-hand position, it closes communication between the tubes I40 and MI and also closes communication between the tubes I46 and I".

Since the valve I5I is in-series with the valve I 36, it follows that the valve I cannot open communication between the pressure supply tube I44 and the tube I06 until the motor speed has reached 900 R. P. M. This prevents a shift to higher gear ratio until the motor is working on an efficient part of its efllciency speed curve. Also, since the valve I40 is in series with the valve I40, it will prevent the valve I40 from opening communication between the pressure supply tube I50 and the tube I42 until the motor speed has reached 1200 R. P. M. where it will still be working on an eflicient part of the motor elliciency speed curve. If desired, the valves I40 and II may be omitted, together with their function. The valves I40 and I40 are interconnected so that, when one valve is opened, the other is closed.

In operation, if it is assumed that the shaft I02 is initially stationary and that the drag of the shaft I02 is such that the turbine rotor II2 will pick up in speed with respect to the pump rotor I08, it will come to pass that the speed of the shaft I02 with respect to the shaft IOI will become equal to and greater than .6. At this point, the gear I29 will cease to pull on the gear I21 and will begin to drag. This will cause the gear I 21 to thread itself along the shaft I22 and move from its left-hand position to its righthand position. This will open the valve I36. If, in the meantime, the speed of the motor shaft IIII has become greater than 900 R. P. M., the valve I5I also will be open. This will admit fluid under pressure to the actuator H9 which will connect the clutch plate II5 with the clutch respect to the speedometer shaft I and will eventually reach a condition in which the pinion III will cease to exert a pull on the gear I20 and will exert a drag. The pitch diameter of the gears I26 and I00 may be so designed that this change from pull to drag will take place at a speed ratio'of driven shaft with respect to drive shaft of .82. This will correspond to an eillciency on the part of the hydraulic portion of the transmission of approximately .8. When this change from pull to drag of the pinion I00 takes place, it will cause the gear I26 to shift laterally as described above and will open the valve I40 and close the valve I43. If the speed of the motor shaft IOI has by this time reached 1,200 R. P. M., the valve I40 will be open. The opening of the valves I40 and I40 will connect the actuator ill with the fluid pressure I50 and will connect the clutch plate II4 with the clutch housing Hi. It will be noted that the shift to the. right of the shifter arm I24 has closed the valve I40 so that the actuator H9 is no longer activated. The above condition will free the clutch plate H5 and connect the clutch plate II4 to the clutch housing IIO, thus causing a direct drive between the shaft IIII and I02 as above described. The valve I described above may be operated manually or by abnormal movement of the auxiliary pedal. Its use is to superimpose a manual control. For overdrive, this valve I45 is shifted to the left. This will cut oil the actuator II8 from its source of supply and will connect the actuator I2I with'its source of supply. This will cause the release of the clutch plate H4 and the application of the brake I20 to effect overdrive. If the valve I45 is shifted to the right, it will cut oil the actuator I I8 as well as the actuator I2I from its pressure supply. This will cancel both the overdrive and the converter has to be considered. In a couhousing II3, thus connecting the pump rotor I08 with the sun gear I05. This will change the transmission condition from the first condition described to. the second condition, in which there is a divided flow of power between the shaft IOI and I02, approximately two-thirds going through the ring gear I01 and the other third going through the sun gear I05 and the hydraulic part of the transmission. This change in condition of the transmission will at first cause a considerable drop in the speed ratio of the turbine rotor II2 with respect to the pump rotor I08 which will cause the hydraulic part of the transmission to begin operating on a different point of its efliciency curve from the point on which it had been previously operating. This point on the efllciency curve may be a point which corresponds approximately with a speed ratio of the driven shaft with respect to the drive shaft of .4. It will be noted that this is still a high point on the efliciency curve of the torque converter. If the drag of the drive shaft I02 is such that it will again start to catch up in speed with the pump rotor I08, the speedometer shaft I23 will continue to catch up in speed with pier, at high speeds of both pump and turbine, the torque increases rapidly with the slip.

The transmission part of the apparatus, as shown, comprises a drive shaft I5I, a driven shaft I52, an intermediate shaft I53, a pump rotor I54, a gear carrier I rotatable with the pump rotor, planet gearing I56 mounted on the gear carrier, a ring gear I51 meshing with the planet gearing and keyed to the drive shaft I5I, a sun gear I50 meshing with the planet gearing, a clutch housing I50 rotatable with the sun gear, a one-way anchor I60 for preventing reverse rotation of the sun gear, a clutch plate I6I splined to the gear carrier and connectible and disconnectible with respect to the clutch housing I59, an anchor plate I62 splined on a fixed anchor ring I63 and connectible and disconnectible with respect to the clutch housing. a fluid pressure actuator I64 which, when supplied with fluid, connects the clutch plate I6I with the clutch housing I50 and which, when not supplied with fluid, connects the clutch housing to the anchor plate I62, a gear carrier I65 keyed to the driven shaft I52; planet gearing I66 mounted on the gear carrier, a turbine rotor 6a, a sun gear I6I keyed to the intermediate shaft I68, a ring gear I68 meshing with the planet gearing, a one-way anchor I69 for preventing reverse rotation'of the'ring gear, a clutch housing I10 rotatable with' the ring gear I68, a clutch plate "I splined on the driven shaft I52 and connectible and disconnectible with respect to the clutch housing I10, an anchor plate I12 splined on the fixed anchor ring I13 and connectible and disconnectible with respect to the clutch housing I10, and a fluid pressure actuator I14 which, when supplied with fluid pressure, connects the clutch plate "I with the clutch housing I10 and which, when not supplied with fluid pressure, causes the anchor plate I12 to be connected with the clutch housing.

This construction enables four diflerent gear speed ratios to be obtained. For low gear, fluid is not supplied to either of the actuators I64 and I14 and hence both anchor rings I63 and I18 are connected to the clutch housings I59 and I10, respectively. In this condition, the ring gear I66 is held against. rotation and the sun gear I58 is held against rotation. The power flow is from the drive shaft. IIa through the ring gear I51, planet gear I56, gear carrier I55, pump rotor I54, turbine rotor I66a, intermediate shaft I58, sun gear I61, planet gearing I66, and gear carrier I65 to the driven shaft I52.

The front planetary may be designed to give a speed reduction of .7 and'the rear planetary may be designed to give a speed reduction of .4.

The combined reduction will amount to .28. For

the next higher gear, fluid pressure is supplied to the front actuator I64 which will connect the sun gear I58 and gear carrier I55 to rotate as a unit with the ring gear I51. This will cause the front planetary to rotate as a unit and will give an overall speed reduction of .4. For the next higher stage, fluid is cut off from the front actuator I64 and is supplied to the rear actuator I14. This will cause the rear planetary to rotate as a unit and will result in an overall speed reduction of .7. For direct drive, fluid pressure is the action of the friction driven gear I14 will change from a pull to a drag at a point where the slip of;the turbinewith respect to the pump is approximately 2% per cent. When the slip of supplied to both actuators I64 and I 14, causing both planetaries to rotate as units. I

The control mechanism forthe transmission comprises three sets of four gears each, each set being similar in general to the four gears shown in Fig. 8. The friction driven gears I 14, I15, I16, I11, I18, and I19 are mounted on a shaft I80 driven from the front speedometer drive I8I and the internally threaded gears I8 I, I82, I88, I84,

I85, and I86 are mounted on a threaded shaft I81 driven from the rear speedometer drive I 88. The pitch diameters of the gears I15 and I82 are so designed that the action of the friction driven gear I15 will change from a pull to a drag at a point where there is approximately 2 per cent slip between the pump rotor I54 and the turbine rotor I66a. This will cause the gear I82 to shift to the right, as shown in Fig. 10, and open the valve I89 to supply fluid under pressure from the pressure inlet I90 to a pipe I9I leading to the lefthand actuator I64. This will cause theactuator I64 to connect the sun gear I58 to rotate with the gear carrier I and will step up the gear part of the transmission from a .24 ratio to a .4 ratio. down of the turbine rotor I66a with respect to the pump rotor, but the turbine rotor will begin This will result in a temporary slowing per cent.

are so designed that under the latest assumed condition of the gear part of the transmission (that is to say, the drive immediately above low) the turbine becomes less than 2 per cent., the gear I8I will moveto the right, as shown in Fig. 11, the shifter arm I92 engaging and closing the valve I93, which is in series with the previously opened valve I89, but opening another valve I84 which will continue to cause pressure to be supplied from the pressure supply I to the actuator I64. The purpose of this valve I84 is to enable the controller to return the transmission to -low gear if the slip should again become more than 2 per cent., If the slip should become more than 2 per cent., the gear I8I will shift back to the left, leaving the valve I93 as shown in Fig; 12, closing the valve I94, cutting off pressure from the actuator I64, disconnecting the clutch plate I6I and connecting the anchor plate I62, to return the transmission to low gear. If, instead of the above suggested increase in slip to more-than 2 per cent., the slip should decrease to 1% per cent., the gear I84 will shift to the right, admitting fluid under pressure to the pipe I95.

The shifting of the gear I84 to the right'shifts the valve I89a to supply pressure to the tube I which leads to the right-hand actuator I14 and also closes the valve I96 to cut '01! pressure from the actuator I64. This connects the clutch plate I 1| with the clutch housing I10 and connects the clutch housing I59 with the anchor plate I62. Under these conditions the rear planetary rotates as a unit and the overall gear ratio is .7. This change in the overall gear ratio will result in a temporary slowing down of the turbine rotor with respect to the pump rotor but the turbine rotor will start to catch up with the pump rotor.

The pitch diameters of the gears I16 and I83 are so designed that under the above condition of the gear part of the transmission (that is to say, the drive immediately below direct drive), the action of the friction driven gear I16 will change from a pull to a drag at a point where' the slip of the turbine with respect to the pump is 3 per cent. When the slip of the turbine becomes less than 3 per cent., the gear I83 will move to the right, the shifter arm I92a engaging and closing the valve I93a which is in series with the previously opened valve I89a but opening another valve I94a which will continue to cause pressure to be applied to the tube I 95 and the actuator I14. The purpose of this valve I9 Ia is to enable the controller to return the transmission from the next-to-high stage to the next-to-low stage if the slip should again become more than 3 per cent. If, however, the slip should continue to decrease so as to become lessthan 1% per cent., the gear I86 will shift to the right, supplying pressure to the tube I9Ia which is in parallel with the tube I9I and, like it, supplies pressure to the actuator I64. The gears I18 and I85, operating in a manner similar to the pair of gears I14 and I8I, serve to change the transmission from direct drive to the next stage below direct drive if the slip should become more than 1% The construction shown in Fig..l4 comprises a duplex clutch I96a, the driving member I91 of which may be driven from a motor, a driven disc 202 is secured, a stator 203, and a turbine rotor 200 having a one-way clutch connection 205 with the driven shaft. The construction is 202 is disconnected to eliminate the action of the hydraulic part of the transmission, and the other clutch disc I99 is connected to drivethe driven shaft I98 direct from the driving clutch member. Suitable antifrlction bearings 200 are provided. I

For controlling the action of the duplex clutch, a rock lever 201 is provided mounted on a rock shaft 208, The transmission from this rock shaft to the clutch comprises a rock yoke 203 secured to the rock shaft 208, an axially movable shifting yoke having a pivoted and sliding connection with the shifter yoke 2), a shifter ring 2" rotatable with the clutch I961; and having a ball bearing swivel connection 2I2 with the shifter yoke 2I0,' a plurality of links 2|3 pivotally mounted on the shifter ring, a plurality of rockers 2| pivotally mounted at 2I5 on the clutch, a plurality of bifurcated rockers 2|6 pivotally mounted at 2" on the clutch and engageable by rollers 2|8 on the rockers, and a plurality of links 2I9 pivotally connecting the bifurcated rockers 2|1 with the shiftable pressure plate 220 which lies between the two driven clutch discs I99 and 202.

When the yoke 2") is shifted to the right, the lower end of the rocker 2 is moved to the right, the antifrlction roller 2I8 on the upper end of the rocker is moved to the left, and the upper end of the bifurcated rocker 2" is moved to the right, thus moving the link 2|9 and pressure plate 220 to the right to grip the driven friction disc 202 between the pressure plate 220 and the right-hand side of the driving clutch member I 91. When the shifting yoke 2I0 is moved to the left, the lower end of the rocker 2 is moved to the left, the antifrlction roller 2I8 is moved to the right and the upper end of the bifurcated rocker 2 I1 is moved to the left, pushing the pressure plate 220 to the left to release the right-hand clutch disc 202 and to grip the left-hand clutch disc I99 between the pres sure plate and the left-hand side of the driving clutch member. In order to effect a yielding spring-pressed engagement of the pressure plate on the clutch disc, the antifrlction rollers 2I8 are mounted on plungers which are spring pressed upwardly by means of coil compression springs 22|.

For controlling the shifting lever, a pair of pressure-controlled cylinders and pistons are provided, the lower piston 222 having a plunger head 223 engageable with an antifrlction roller 224 on the lever 201 and the upper piston 225 having a pressure head 226 engageable with another antifriction roller 221 on the lever. A coil tension spring 228 is provided, tending to hold the lever 201 in its right-hand position. The lower longer cylinder is controlled primarily by a valve 228, the position of which is determined by the relative speed between the pump rotor and the turbine rotor. The apparatus by which the position of the valve is controlled is similar to that shown in Fig. 8, comprising the shaft I22 I30 meshing with the gear I20, the friction 001- I lar; I32, the washers I3I, the coil compression spring I33, and the shifter arm I30 connected.

with the valve 223.

Assuming that the valves 230 and BI are in position to connect the tubes 232 and 233, the operation of the valve shifting gears I20 and I00 is substantially the same as that described in connection with Fig. 8. When the speed ratio of'the driven shaft I00 with respect to the pump rotor 200 reaches a predetermined value, the gear I30 will cease-to exert a pull on the gear I20 and will begin to exert a drag. This will cause a helical motion of the gear I20 on its shaft I22 and will cause it to thread to the right until it engages the stop collar I28a. This shift of the gear I20 to the right opens the valve 220, admitting pressure to the pipe 230 leading to the long cylinder This will force the lever 201 to its extreme left-hand pomtion, thus shifting the yoke 2|0 to its extreme left-hand position, causing the upper end of the antifrlction roller 2I0 to move to its extreme right-hand position and force the pressure plate 220 to its extreme lefthand position, releasing the clutch plate 202 connected with the pump rotor and connecting the clutch plate I90 secured to the driven shaft I80. Thus, at a definite point in the changing speed ratio of driven shaft with respect to pump rotor, the hydraulic part of the transmission will be disconnected and the driven shaft will be-connected directwith the driving member of .the clutch. By this apparatus the inemcient portion of the efficiency curve of the hydraulic torque converter may be eliminated,

The lower one ofthe auxiliary control valves 21 is provided in order to return the control lever to the neutral position shown in the drawings when the accelerator pedal is released. To accomplish this the valve 23| is provided with a port 230 which, when the valve is in its righthand position, will connect a pressure supply pipe with the pipe 235 leading to the upper cylinder and is also provided with a port 230 which, when the valve is in its left-hand position, will connect the pressure passage 232 with a tube 233 leading to the lower cylinder. A coil tension spring 231 is provided which tends to hold the valve in its left-hand position. This valve 23I is controlled by means of slide rod 200 which is directly connected with the accelerator pedal. When the accelerator pedal is released, the pedal spring 230 will cause the slide rod 238 to move to its extreme right-hand position, which will close the port 230 and open the port 230. This will supply pressure to the piston 22! and cause the plunger 220 to move the lever 201 to neutral position, in

- which the pressure plate 220 will be in its central positio leaving both clutch discs disconnected. As soon as pressure is applied to move the accelerator pedal to the left, the slide rod-239 connected with it will be moved to the left, allowing the spring 231 to move the valve'-'23I to its lefthand position, in which the port 230 will be closed and the port 238 will be open to connect the pressure passage 232 with the tube 233 leading to the lower cylinder. Then, if the valve 220 is open, pressure will be supplied from the pressure line 232 to the lower cylinder as soon as the valve 229 has been moved to the right by the helical movement of the gear I26. The upper valve 230 is provided to enable the operator to shift from direct drive to hydraulic drive when desired, by an abnormal movement of the accelerator pedal. This abnormal movement will move the slide rod 238 to a position in which its pressure head 240 will engage a pressure head 24I an another slide rod 242, which auxiliary slide rod has a lost motion connection with the valve 230. Thi excess or abnormal movement of the slide rod will close the valve 230, cutting off the supply of pressure to the lower cylinder and enabling the coil tension spring 228 to return the control lever 201 to its right-hand position, in which the hydraulic part of .the transmission will be brought into play. This slight normal leakage past the pistons 222 and 225 and at the valve 23I will in general enable fluid to escape to enable the pistons to return under the action of the. spring 228. This condition will be maintained at least until the accelerator pedal is released sufficiently to enable the spring 243 to cause the auxiliary slide rod 242 to move to the right to take up the lost motion in its connection with the valve and finally to open this valve. This will place the transmission again in condition for control by means of the gears I26 and I30. It should be stated that the transmission and clutch are shown approximately to one-fourth scale, while the gears and valves are shown approximately in full scale.

The construction shown in Fig. comprises a in Fig. 15 comprises the pressure plate 251 connected by links 268 to bifurcated rockers 269 which also may be controlled by the rockers 2I4. The contour of the bifurcated rockers 259 engageable with the rollers 2I8 i different from that of the bifurcated rockers 2I6 including an extension 260 so formed that the final movement of the rollers 2I8 will effect a shift of the bifurcated rockers 259 to move their upper ends to the rightto cause the pressure plate 251 to pinch the clutch disc I99 against the other pressure plate 220, thus causing both clutch plates I99 and 202 to rotate simultaneously with the driving clutch head.

With this construction, when the lever 201 is in neutral position, both of the clutch plates I99 and 202 will b disconnected. When the upper end of the lever 201 is moved to its forward lefthand position, the clutch pressure plate 220 will also be moved to its forward position to connect the clutch plate I99 to the driving head I91. This will cause the sun gear 246 to rotate, the ring gear clutch plate being free to rotate forwardly but being held against reverse rotation by the one-way anchor 26I. This will give a low speed drive to the ,driven shaft 249. When pressure is supplied to the piston 262 in the upper cylinder 263, the clutch controlling lever 201 will duplex clutch I96b, similar to the duplex clutch l96a shown in Fig. 14, having a driving member I91, which may be driven from a hydraulic coupler 244, .an intermediate shaft 245 to which one of the clutch discs I99 is secured, a second driven clutch disc 202 splined on the sleeve 245a,

a planetary gear construction comprising a sun gear 246 keyed on the shaft, a ring gear 241 fast -on the sleeve 245a, a gear carrier 248 keyed to the driven shaft 249, planet gearing 250 mounted on the gear carrier 248 and meeting with the sun gear 246 and ring gear 241, a second sun gear 25I held against reverse rotation by means of the one-way anchor 252, a second set of planet gearing 253 meshing with the sun gear 25I and ring gear'241, and control apparatus for the clutches similar to the control apparatus shown in Fig. 6 comprising the friction wheel 89, the shaft having a universal joint connection 94, on which the friction wheel 89 is splined, th friction disc- 95, the rock arm 92 shifted by the friction wheel 89, and the rock shaft 88. The friction disc is driven-from the front speedometer drive shaft 16 and the friction wheel 89 is driven from the rear speedometer drive shaft 11.

Th hydraulic coupling 244 comprises the pump rotor 254 keyed to the motor shaft 255 and the additional pressure plate 251 and control means therefor. The rock lever 201, the rock shaft 208,

- the rock'yoke 209. the shifter yoke 2I0, the shifter ring M I, the swivel connection 2I2, the links M3, th rockers 2I4, the bifurcated rockers 2I6, the rollers 2I8, the links 2I9, and th pressure plate 220 may be substantially the same as that shown in Fig. 14. In addition to these, the clutch shown be moved to the right a suflicient distance to release the front clutch plate I99 and connect the rear clutch plate 202, disconnecting the sun gear 246 and connecting the ring gear241. Under these conditions, the rear sun gear 25I wil1 be held against reverse rotation by the one-way anchor 252 and the driven shaft 249 will be driven at an intermediate speed by the ring gear 241, the planet gearing 253 and the gear carrier 248 secured to the driven shaft.

If fluid pressure is admitted to the piston 264 of the lower cylinder-265, the clutch lever 201 will be moved still further to the right, causing the pressure plate 251 to be moved to the right willciently to grip the front clutch plat I99. Under this condition, with both the sun gear 246 and ring gear 241 connected to rotate with the driving head I91, the drive will be direct, the planetary glgairing rotating as a unit with the driving head Th two pistons 262 and 264 are controlled by the control mechanism previously referred to which includes, in addition to the parts previously described, a valve 266 controlling the supply of .pressure to the upper cylinder 263, a valve 261 controlling the supply of pressure to the lower cylinder 265, a rock arm 268 pivotally mounted at 88 and having a finger 269 for engaging with arms 210 on the valve 266, a rock arm 21I pivotally mounted at 88 having a finger 212 engaging the arms on the other valve 261, and a spring arm 213 frictionally engageable with arcuate friction surfaces 214 and 215 on the arms 261 and 21I, respectively.

As described, in connection with Fig. 6, the

friction wheel 89 will adjust itself along the surface of the friction disc 95 until its peripheral speed equals the surface speed of that portion of the disc 95 which it engages. As the driven shaft 249 increases in speed, the friction wheel 89 will move to the right, causing the upper end of the spring friction arm 213 to move to the left. In its movement to the left, it will actuate the rock arm 268 to move this rock arm to the left, opening the valve 266 supplying pressure to the upper short stroke piston 262. This supply of pressure to the upper short stroke piston will move the upper end of the clutch lever 201 to the right sufficiently to disconnect the front clutch plate I99 and connect the rear clutch plat 202. This will effect a shift from low to intermediate gear. If the speed of the driven shaft 249 continues to increase in speed with respect to the drivin shaft 265, the friction wheel 89 will shift still further to the right and will eventually move the spring friction finger 213 into engagement with the arcuate surface 215 of the left-hand rock arm 21l, causing the valve 261 to open and admit pressure to the long stroke piston 264. This will move the clutch lever 291 still further to the right and cause the clutch pressure plate 251 to grip the front friction plate I99 and press it against the other pressure plate 220 to cause the sun gear 2 as well as the ring gear 241 to rotate with the driving clutch head I91, thus effecting a shift from intermediate to high.

The purpose of the frictional engagement between the sprin friction arm 213 and the friction surfaces 214 and 215 is to eifect a closing of the valve by a movement of the spring arm to the right which might be desirable in case the speed of the driven shaft with respect to the drive shaft should begin to decrease.

Further modifications will be apparent to those skilled in the artand it is desired, therefore, that the invention be limited only by the scope of the appended claims.

Having thus described my invention, what I claim and desire to secure by Letter Patent is:

1. A transmission and controller comprising a hydraulic transmission mechanism including a pump rotor and a turbine rotor driven by said pump rotor and having an infinitesimally-variable speed ratio with respect thereto, a two-stage positive transmission mechanism in series power flow relation with respect to said hydraulic transmission mechanism, each stage having a fixed definite speed-transmitting ratio, and means for transforming said positive transmission mechanism from one stage to the other controlled as to time of transformation by the variation in speed ratio of the turbine rotor with respect to the pump rotor, comprising an actuator for selectively conditioning the positive transmission mechanism for its two stages, and means controlled by the relative speed of the rotors for controllin the time of operation of said actuator comprising means driven in timed relation to the pump rotor and means driven in timed relation to the turbine rotor.

2. A transmission and controller comprising a hydraulic transmission mechanism including a pump rotor, a turbine rotor driven by said pump rotor and having an infinitesimally variable speed ratio with respect thereto, and a reaction stator acting between said pump rotor and turbine rotor, a two-stage positive transmission mechanism in series power flow relation with respect to said hydraulic transmission mechanism, each stage having a fixed definite speed-transmitting ratio, and means for transforming said positive transmission mechanism from one stage to the other controlled as to time of transformation by the variation in speed ratio of the turbine rotor with respect to the pump rotor comprising an actuator for selectively conditioning the positive transmission mechanism for its two stages, and means controlled by the relative speed of the rotors for controlling the time of operation of said actuator comprising means driven in timed relation to the pump rotor and means driven in timed relation to the turbine rotor.

3. A transmission and controller comprising a hydraulic transmission mechanism including a 5 pump rotor and a turbine rotor driven by said pump rotor and having an infinitesimally variable speed ratio with respect thereto, a two-stage positive transmission mechanism in series power flow relation with respect to said hydraulic l0 transmission mechanism, each stage having a fixed definite speed-transmitting ratio, and means for transforming said positive transmission mechanism from one stage to the other controlled as to time of transformation by the vari- 15,ation in speed ratio of the turbine rotor with respect to the pump rotor, comprising an actuator for selectively conditioning the positive transmission mechanism for its two stages, and means controlled by the relative speed of the rotors for controlling the time of operation of said actuator comprising means driven in timed relation to the pump rotor and means driven in timed relation to the turbine rotor, said positive transmission comprising a three-element planetary gearing coaxial with'said rotors and said actuator comprising a clutch member connectible and disconnectible with respect to on of the elements of the planetary gearing for controlling its rotation.

4. A transmission and controller comprising a hydraulic transmission mechanism including a pump rotor and a turbine rotor driven by said pump rotor and having an infinitesimally-variable speed ratio with respect thereto, a two-stage positive transmissionmechanism in series power flow relation with respect to said hydraulic transmission mechanism, each stage having a fixed definitespeed-transmitting ratio, and means for transforming said positive transmission mechanism from one stage to the other controlled as to time of transformation by the-variation in speed ratio of the turbine rotor with respect to the pump rotor, comprising an actuator for selectively conditioning the positive transmission mechanism for its two stages, and means controlled by the relative speed of the rotors for controlling the time of operation of said actuator comprising means driven in timed'relation to the pump rotor, means driven in timed relation to the turbine rotor, two intermeshing gears driven by said timed means respectively, and means whereby when the relative speed of said timed means reachesa predetermined ratio -said gears will operate to cause said actuator to effeet a transformation in the positive transmission.

5. A transmission and controller comprising a hydraulic transmission mechanism including a pump rotor and a turbine rotor driven by said pump rotor and having an infinitesimally-variable speed ratio with respect thereto, a two-stage positive transmission mechanism in series power flow relation with respect to said hydraulic transmission mechanism, each stage having a fixed definite speed-transmitting ratio, and means for transforming said positive transmission mechanism from one stage to the other controlled as to time of transformation by the variation in speed ratio of the turbine rotor with respect to the pump rotor, comprising an actuator for selectively conditioning the positive transmission mechanism for its two stages, and means controlled by the relative speed of the rotors for controlling the time of operation of said actuator comprising means driven in timed relation to the pumprotor, means driven in timed relation to the turbine rotor, two intermeshing gears driven by said timed means respectively, and means whereby when the relative speed of said timed means reaches a predetermined ratio said gears will operate to cause said actuatonto efi'ect a transformation in the positive transmission, one oi said gears being frictionally driven and the other having a lost motion helical engagement with its timed drive means.

6. A transmission and controller comprising a hydraulic transmission mechanism including a pump rotor and a turbine rotor driven by said pump rotor and having an infinitesimally-variable speed ratio with respect thereto, a two-stage positive transmission mechanism in series power flow relation with respect to said hydraulic transmission mechanism, each stage having a fixed definite speed-transmitting ratio, and means for transforming said positive transmission mechanism from one stage to the other controlled as to time of transformation by the variation in speed ratio of the turbine rotor with respect to the pump rotor, comprising an actuator for selectively conditioning the positive transmission mechanism for its two stages, and means controlled by the relative speed of the rotors for controlling the time of operation of said actuator comprising reciprocable means positioned in accordance with the relative speed of said rotors.

7. A transmission and controller comprising a hydraulic transmission mechanism including a pump rotor and a turbine rotor driven by said pump rotor and having an infinitesimally-variable-speed ratio with respect thereto, a two-stage positive transmission mechanism in series power flow relation with respect to said hydraulic transmission mechanism, each stage having a fixed definite speed-transmitting ratio, and means for transforming said positive transmission mechanism from one stage to the other controlled as to time of transformation .by the variation in speed ratio of the turbine rotor with respect to the pump rotor, comprising an actuator for selectively conditioning the positive transmission mechanism for its two stages, and means controlled by the relative speed of the rotors for controlling the time of operation of said actuator comprising reciprocable means positioned in accordance with the speed of said pump rotor, and reciprocable means positioned in accordance with the speed of the turbine rotor. v

8. A transmission and controller comprising a hydraulic transmission mechanism including a pump rotor and a turbine rotor driven by said pump rotor and having an infinitesimally-variable speed ratio with respect thereto", a two-stage positive transmission mechanism in series power flow relation with respect to said hydraulic transmission mechanism, each stage having a fixed definite speed-transmitting ratio, and means for transforming said positive transmission mechanism from one stage to the other controlled as to time of transformation by the variation in speed ratio of the turbine rotor with respect to the pump rotor, comprising an actuator for selectively conditioning the positive transmission mechanism for its two stages, and means controlled by the relative speed of the rotors for controlling the time of operation or said actuator comprising a first friction rotor driven in timed relation to one of said hydraulic, rotors, and a second friction rotor engaging said first friction rotor driven in timed relation to the other hydraulic rotor and self-adjusting with respect to said first rotor to a non-slip position.

L. POLLARD. 

